KR20190042069A - Lever type Brake device - Google Patents

Abstract

In the lever type braking device, the actuating means is realized in the form of a screw jack (19) with an electric motor (20) and an angle gear (21), the angle gear comprising a jack The screw 22 is driven. The load sensor 29 coupled to one of the levers controls the force applied in the brake mode via the power regulating means 25. [ The position sensor 31 coupled to the other lever determines the positions of the lever in the idle mode.

Description

Lever type Brake device

The present invention relates to a brake device suitable for slowing or stopping the rotation of a rotary shaft or for stopping or slowing the movement of a vehicle or apparatus along a rail. The braking device of the present invention is used in association with a rotary shaft for holding a radial disk or flange in rotation between brake pads of a braking device, or in a non-braking mode, Quot; is intended to be used in connection with a vehicle or apparatus that moves along a rail extending into a " rail "

In particular, the present invention relates to a lever type braking device comprising a left lever journaled for pivotal motion about a first axis, a second lever about a second axis circumferential parallel to said first axis, And the shafts divide each lever into a short lever length and a long lever length. The left and right brake pads are journaled pivotally to the short lever lengths of the left and right levers, respectively. The actuating means may be configured to engage with the long lengths of the levers and be operable to pivot the levers in opposite rotational directions about the respective axes and the actuation means may control movement of the brake pads between the brake position and the idle position, Generating a clamping force exerted by the brake pads upon actuation.

A second aspect of the present invention is to provide a structure and functional means for positively locking the rotary shaft against rotation on the one hand at a set pivot position and, on the other hand, a pivoting position of the rotary shaft, To a brake mechanism of an assembly integrated with a shaft rotation mechanism configured to rotate the shaft.

The braking device of the present invention may refer to a category of lever brakes configured to stop and / or hold the application. It has a wide range of applications by being designed for braking forces in the range of several thousand Newton (N) to several hundred kilo Newtons (kN), for example in wind power plants for stopping rotation of propellers or turbines, .

Although the force of the brake is generated by hydraulic pressure in the most traditional application, other applications may require alternative power to avoid the consequence of hydraulic fluid circuit leakage.

In the past, disk brake designs have attempted to replace hydraulic power with electrical power. For example, European Patent Application EP 2 500 597 A1 discloses a disc brake construction for a wind power plant wherein the electric motor activates the brake through a worm gear transmission, which worm gear transmission drives the spindle And a planetary roller screw that is driven toward the brake pads in an axial translation.

One problem that needs to be solved in applying electric power to disc brakes for rotary shafts is the vibration of the rotor, which can be transmitted to the motor through components of the brake pads and the power transmission. This vibration, in addition to causing wear in the rotating parts and bearings of the motor, can change the position of the gears, and consequently, the brake force may be lost. In hazardous environments, safety may be compromised if vibration is allowed to cause involuntary application of the brakes.

In an application of an aircraft rotor or propeller, US Application US 2014/0231188 A1 discloses a rotary shaft brake system with lever type brakes comprising an elastically bendable lever. In the brake mode as well as the idle position, the bending lever is forced into a state deformed by the linear actuator engaged with the levers. Thus, in order to avoid vibratory and involuntary braking, the bending lever is constantly cured under stress by an electrically powered actuator.

Although the metal or steel is inherently elastic, metal or steel elements that are constantly cured under a deforming load will ultimately undergo crystal structure changes and fatigue of the material, resulting in a reduction in bending resistance. In applications of lever brakes, a gradual reduction in bending resistance can potentially affect the force of the clamping applied in the brake mode. In US application US 2014/0231188 Al, the force of clamping is controlled by measuring the bow of the lever capable of braking during braking. However, over time, the degree of bending is caused by the braking deformable brake levers The brake effect and the true value of the clamping force.

It is an object of the present invention to provide an alternative lever type braking device that is operated by an electromotive force.

It is a particular object of the present invention to provide an electric power lever type brake device with a control of a clamping force, which is advantageous in that the force multiplying brake lever made of metal, such as steel, It does not receive.

It is another object of the present invention to provide a braking device with an integral, electrically assembled assembly as a whole which includes structural and functional means for stopping, maintaining and / or rotating the rotary shaft as desired during installation or maintenance I have.

At least a first object is substantially satisfied by a lever type braking device as initially described, wherein the actuating means is implemented in the form of a screw jack, which comprises an electric motor and a jack coupled between the levers And an angle gear for driving the screw. A load sensor coupled to one lever controls the force applied in the brake mode through power regulating means. A position sensor coupled to the other lever determines the lever positions in the idling mode.

An essential feature of the invention is the use of force multiplying levers, which not only reduces the need for power effects as a result of leverage, but also reduces the ratio of lever lengths and the resulting stroke of the jack Due to its length, it also provides more precise control and regulation of the force exerted through the rotary motor shaft. The relationship of the lengths between the long lever length on one side of the fulcrum and the short lever length on the other side is preferably 3: 1 - 1 to provide a lever ratio in the range of 2: 1 to 6: 1, A ratio of levers in the range of 5: 1, and most preferably about 4: 1.

Another advantage is achieved by the selection of a screw jack with an angle gear drive as proposed. The angle gear drive may be integrated into the lever system and the length of the jackscrews, as opposed to a linear drive typically on the left or right of the lever configuration, should be installed in the direction of the force actually applied by the actuator Lt; RTI ID = 0.0 > orientation < / RTI > of the motor.

It will be appreciated by those of skill in the art that the solution of the present invention can be sized for a variety of different applications and can also be used in calculations of a particular design to determine motor strength, screw jack gear ratio, lever ratio, brake pad area and brake pad friction coefficient Etc. will be used by those skilled in the art. Thus, for the purposes of the present disclosure, it is neither necessary nor useful to specify in detail the range of values that can be applied for each parameter of interest. However, since the angle gear drive is an essential feature of the present invention, angle gear ratios in the range of 5: 1 to 50: 1 are disclosed as desirable design parameters.

Another advantage achieved by the presently disclosed and claimed invention is the high accuracy and consistency in measurement, which is provided by a sensor that records the force exerted from the actuator rather than the resulting effect on the lever. Regardless of any characteristic changes in the lever material, whether due to fatigue, temperature or other causes, the brakes always provide the force of clamping, which is multiplied by the lever ratio and registered by the load sensor.

Another advantage is that the air gap between the brake pads and the interposed brake disc or flange can be easily set in idle mode by simple adjustment of the position sensor. The expansion of the air gap resulting from wear of the friction elements in the brake pads can be easily compensated by the same means.

The lever assemblies are journaled in brackets in a free floating manner which allows the levers to be moved to their respective positions for the clamping force applied uniformly to each side of the brake disc or flange in the brake mode. Is automatically adjusted. In order to ensure that the brake pads are released from the disk on both sides when the brake is released, the pivot limiting means is provided on the brackets as a counter support, so that only upon return to the idle position, . This pivot limiting means on the bracket is adjustable and is adjusted to provide some freedom of movement to the levers even in the idle position. In this way, the levers are completely released from stress at the idle position.

An elastic member such as a tension spring may be connected between the lever and its associated bracket. The elastic member is effective, if appropriate, to prevent spontaneous swinging of the levers at the idle position, thus counteracting vibration and noise in the lever arrangement.

Brake pads are pivotally supported on the mutually facing inwardly facing sides of the left and right levers. The tension spring and pivot restricting portions ensure that the brake pads are maintained in a parallel relationship in the idle position, respectively. The pivot restricting portion is preferably adjustable to allow parallel control between the brake pads and the brake disc / flange.

The angle gear of the screw jack includes a worm screw on the motor shaft and a gear wheel on the jack screw. The interlocking threads can be designed to provide self-locking engagement to maintain the clamping force in break mode. Return of the brake pads from the brake position to the idle position can be achieved by reversing the direction of rotation of the electric motor.

If a self-locking arrangement on the angle gears is not used, a motor with an electro-mechanical brake or an electromagnetic brake acting on the motor may be used instead to maintain the clamping force applied in the brake mode.

With respect to the structural design of the components of the brake, it should be mentioned that the cross-sectional area of the lever, in particular the thickness dimension, can be constituted by a gradual and continuous reduction, which forms a taper in the long length of the lever. Combined with smooth surfaces avoiding any kind of indication that could lead to failure, the taper in the lever achieves a uniform and favorable stress distribution when the brake is applied.

The brakes described so far are independent devices, which can be applied to various situations on their own.

One particularly advantageous embodiment of the braking device is in an assembly with a positive locking and unlocking mechanism which can be configured and operated to engage a rotary shaft by engaging a flange or brake disk fixed to the rotary shaft , In this way, reliably locks the rotary shaft against rotation at the set pivot position.

Another particularly advantageous embodiment of the braking device is in an assembly with a shaft rotation mechanism, the mechanism being configured to adjust the pivot position of the rotary shaft in a standstill manner.

In both cases, the assembly is preferably elongated and has a stand such as a plate, which has a support base at the bottom end.

The stand is adapted to mount left and right brackets on the left and right sides of the stand, respectively. It will be appreciated that in this case the short and long portions of the levers have lengths sufficient to position the brake pads and screw jacks, respectively, outside the opposing front and rear rims of the substantially flat stand.

In a fully integrated solution, all three functions, namely the braking device, the locking and unlocking mechanism and the shaft rotation mechanism, can all be placed and supported on the stand. In such a case, the preferred order at the location on the stand is to place the locking and unlocking mechanism at the lowest end of the stand adjacent to the base support, since this portion of the assembly is expected to deliver the largest load to the stand. For the same reason, the shaft rotation mechanism is preferably disposed at the uppermost end of the stand, leaving a central area of the stand for mounting the braking device.

The locking and unlocking mechanism includes an extendable / retractable plunger that cooperates with a flange or brake disk fixed to the rotary shaft, wherein the brake disk or flange includes a plurality of through holes, Lt; / RTI > in the radial direction of the circumference. The plunger can be electrically operated at extension and contraction by an electric motor and a linear device.

The shaft turning mechanism includes a gear wheel and the gear wheel is rotatably configured with a toothed periphery engageable with a toothed periphery of the flange or brake disk fixed to the rotary shaft. The gear wheel may be electrically rotatable by an electric motor and a bevel gear drive.

Embodiments and details of the present invention will now be described with reference to the accompanying drawings.
1 is a three-dimensional perspective view of a braking device.
Fig. 2 is a partial sectional view from above of the braking device of Fig. 1, taken along the plane II-II of Fig.
3 is a three-dimensional perspective view of an integrated assembly including the braking devices of FIGS. 1 and 2;
Figure 4 is a corresponding three-dimensional perspective view of the integrated assembly shown from a different viewing angle.

First of all, in the present invention, " left " and " right " are used for identification purposes only and should not be construed as indicating the absolute direction to the observer.

1 and 2 show a brake device 1 of the present invention. The brake device 1 has a left lever 2 which pivots on the left bracket 3 for swinging movement around a first axis formed by the axle 4 which is seated in the left bracket, (journal). The right lever 5 is pivoted to the right bracket 6 in such a manner that it is pivoted for swinging movement about a second axis formed by the axle 7 mounted on the right bracket. The brackets 3, 6 are configured to be mounted on opposite sides of the support structure as illustrated below.

The axles 4,7 define left and right fulcrums which divide the levers into long lever lengths 2 ', 5' and short lever lengths 2 "and 5", respectively (see FIG. 2) ). In the embodiment shown in Figures 1 and 2, a long lever length 2 ', 5' is formed with a tapered thickness w which is continuously reduced from individual points towards the ends of the levers do. It is observed that the shape of the levers 2, 5 is such that there is no shape to interrupt the smooth, continuous surface of the levers.

The left brake pad 8 is journaled pivotally on the pivot 9 at the end of the short length of the left lever 2. The right brake pads 10 are journaled pivotally on the pivot 11 at the end of the short length of the right lever 5 in a corresponding manner. In the embodiment shown in Figures 1 and 2 the brake pads are journalled to the hinges 12,13 which hinge against the mutually opposing side surfaces 2i, 5i of the lever < RTI ID = 0.0 > Respectively.

Brake pads 8,10 are each associated with a pivot limiter 14,15 which is located in the idle position, i. E., In the non-braking mode, . In particular, the pivot restricting portion is adjustably arranged to ensure a substantially parallel relationship between the brake pads and the brake disc or flange, as well as between the brake pads, respectively (see brake disc 16 of FIG. 2) Except for air gaps on both sides of the disc in the non-braking mode, it occupies the gap between the brake pads in use. In the illustrated embodiment, the pivot restricting portion is implemented as a threaded bolt (14, 15) that cooperates with the tension springs (17, 18), respectively, and the springs are effective to deflect the brake pads against the pivot restricting portion.

In the brake device 1, the brake power is generated by an electrically operated screw jack 19. The main components of the screw jack 19 are an electric motor 20, an angle gear drive 21 and a jack screw 22. These components hang on the end region of the long lever length of one of the levers, in this case hanging on the end of the left lever 2. The mounting bracket 23 pivotally connects the screw jack to the lever by engaging the screw jack housing 24 on the inwardly facing side 2i of the lever 2.

The motor 20 includes a power control adjustment means 25 and a motor brake 26. The motor output shaft 27 maintains a worm thread that engages with a geared nut 28 which is journaled to the screw jack housing 24 for rotation. The nut has an inner thread that engages the outer thread on the jackscrew. When power is applied to the motor, the rotary nut 28 drives the jack screw in a linear translation in braking the levers to pivot down until the brake pads come into contact with the brake disc or flange. Since the lever assembly with the screw jack 19 is a unit that freely swings on the first and second axles 4,7, the lever assembly will automatically be adjusted for alignment with the brake disc / flange .

A load sensor 29 is configured to control the clamping force exerted by the screw jack 19 in the brake mode. The sensor 29 is a load cell coupled to the right lever 5 and more precisely this is a sensor seat 30 supported in the end region of the long length 5 ' As shown in Fig. The sensor 29 takes a load applied from the jackscrew in the brake mode and generates an electrical signal whose voltage is proportional to the load. The output signal from the load sensor is interpreted as a metric value, which is combined with other metric parameters such as ratio of levers, gear ratio and motor power to determine the clamping force exerted by the brake pads Is used. Such calculations may be made in an external control unit, which is coupled to the motor power control to regulate or interrupt the power supply in response to the execution of a force control sequence programmed into the control unit.

The relative positions of the left and right levers in the idle position are determined through the position sensor 31 connected to the motor power control unit. The position sensor 31 initiates interruption of the power supplied to the motor when the jackscrew 22 reaches a predetermined retracted position in the return from the extended position in the brake mode. The position sensor 31 detects the position of the extreme end 32 of the jackscrew 22 which reaches the housing 33 coupled to the side of the lever facing outward through the opening of the lever 2 . A detachable hatch 23 provides access to a position sensor in the housing to set a triggering position to shut off the power supply to the motor.

The pivot restricting means is provided in the braking device to prevent automatic pivoting of the lever assembly in an idle position. In the illustrated embodiment, the bolts 35, 36 are each fixed to the brackets 3, 6 and are adjustably disposed relative to the inwardly facing sides of the levers, thereby providing the levers with an idle position, Position ensures the formation of air gaps between brake pads and disc brakes or flanges on each side of the disc brake / flange.

The pivot limiting means or bolts 35, 36 may be adjusted for minimum clearance towards the inner sides of the levers. Elastic means such as tension springs (not shown in the drawings) can be disposed between the brackets and levers to prevent vibration and noise if necessary.

The integration of the brake device 1 with the assembly with complementary functions and means will now be described with reference to Figs. 3 and 4. Fig.

The integrated assembly includes a brake device 1, an unlocking mechanism generally indicated at 100 and a shaft rotation mechanism correspondingly indicated at 200. The braking device 1, the locking and unlocking mechanism 100 and the shaft rotation mechanism 200 are supported on a generally flat and plate-like stand 37 which includes a base plate 38 attached to the lower end of the stand, Respectively. In use, the base plate may be bolted to a structural part of an application requiring brake installation.

The integrated assembly is configured to work with a specially designed brake disc 39. The brake disc has a central opening 40 for inserting a rotating shaft (the shaft is omitted in the drawing) in a fixed relationship in rotation between the shaft and the brake disc. Particularly, the special design comprises a toothed periphery 41 and a plurality of through holes 42, which are arranged in a circle, that is to say in a radially inner Are arranged at equal intervals. The through holes 42 can be uniformly spaced along the circle.

The holes 42 are configured to act in conjunction with the plunger of the locking and unlocking mechanism 10. A plunger, not shown in the drawing, is installed in the housing 101 and is mounted in a housing journalled to move from a retracted position in the housing to an extended position in which the plunger is inserted into one of the through holes 42 in the housing 101. Operation of the plunger in extension and retraction is achieved by the electric motor 102 and the linear drive 103.

The tooth periphery 41 of the brake disk 39 is arranged to act in conjunction with a gear wheel 201 journaled to the shaft rotation mechanism 200. The gear wheel 201 can be laterally switched between a working position in which the gear disk is engaged with the brake disk and a rest position in which the brake disk is not engaged. By means of the electric motor 202 and the bevel gear 203, the gearwheel may be engaged and not engaged with the brake disk. In the engaged mode, the gear wheel 201 can be rotated to slowly rotate the brake disk and the shaft fixed thereto. The electric motor 204 is driven and connected to the gear wheel 201 through a bevel gear drive 205 and a gear box 206. [ The gear box 206 is configured to substantially reduce the motor spindle speed to generate a slow rotation suitable for fine adjustment of the rotary shaft position in the installation and maintenance operation. The counter 207 may be configured to control the rotation of the rotary shaft to a single tooth length of the toothed periphery of the brake disk. The motor 204 may be provided with a motor brake 208, which may be applied to a motor spindle, in order to capture the gear wheel and, thus, the brake disk and shaft in the set pivot position.

The braking device of the present invention is advantageously applied to an assembly having a marine vessel propulsion shaft.

Another useful embodiment of the braking device is an assembly with a power generating shaft.

Another useful embodiment of the braking device is an assembly with a mining machine.

Another useful and advantageous embodiment of the braking device is an assembly with a manufacturing process machine.

Another possible implementation of the braking device is an assembly with a vehicle or device moving along the rail.

It should be noted that the advantages for the user and environment are an essential feature of the electric drive for the operating function of the integrated assembly. It will be appreciated that the claimed and described braking device 1 provides an indispensable basis for such achievement.

1. Brake device 2. Left lever
3. Left bracket 5. Right lever
6. Right bracket 7. Second axis

Claims (15)

A left lever 2 journaled to the left bracket 3 for swing motion around the first axis 4;
A right lever 5 journaled to the right bracket 6 for pivotal movement about a second axis 7 parallel to the first axis, the axes being arranged to define a respective lever length 2 "; 5 ") and a long lever length (2 ';5');
A left brake pad 8 and a right brake pad 10 journaled pivotally on short lengths of a left lever and a right lever, respectively;
Actuating means (19) operable to engage the elongated lengths of the levers and to pivot the levers in a contra rotating direction about respective axes (4; 7), characterized in that the actuating means And actuating means (19) for controlling the movement of the brake pads on the brake pads and for generating a clamping force exerted by the brake pads during brake actuation,
The operating means is a screw jack 19 which comprises an angle gear 21 for driving a jack screw 22 coupled between the levers 2 and an electric motor 20, A load sensor 29 coupled to one lever 5 controls the force applied in the brake mode via the power regulating means 25 and a position sensor (31) determines the position of the lever in the idling mode. 2. Brake device according to claim 1, wherein the adjustable pivot limiting means (35, 36) in the brackets (3, 6) provide free movement to the levers (2; 3. A brake lever according to claim 2, characterized in that an elastic member, such as a tension spring, is connected between the lever (2; 5) and the bracket (3; 6) associated with said lever and is effective to prevent automatic pivoting of the levers in the idle position. Device. The brake pads 8 10 are pivotally supported on the mutually facing side surfaces 2i 5i of the left lever 2 and the right lever 5 and the tension springs 17 (18; 18) and an adjustable pivot limiter (14; 15), respectively. The angle gear 21 includes a worm screw 27 and a geared nut 28. The return of the brake pads from the brake position to the idle position is controlled by an electric motor Wherein the threads are designed to provide a self-locking engagement such that only achievable by reversing the direction of rotation of the rotor (20). 6. The braking device according to claim 5, wherein the angle gear (21) has a gear ratio in the range of 5: 1 to 50: 1. In one aspect, the relationship of the length between the long lever length (2 '; 5') and the short lever length (2 "; 5") provides a lever ratio in the range of 2: 1 to 6: 1, Provides a lever ratio in the range of 3: 1 to 5: 1. Wherein the cross sectional area of the lever (s), particularly the thickness dimension (?), Gradually decreases continuously toward the end of the long lever length of the left lever and / or the right lever. The left bracket 3 and the right bracket 6 are respectively supported on the left side and the right side of the stand 37 and the braking device is provided with a positive locking and releasing mechanism 100 Wherein the locking and unlocking mechanism is operable to capture the rotary shaft by engagement with a flange (39) or brake disk disposed on the stand and secured to the rotary shaft. 10. The apparatus of claim 9, wherein the locking and unlocking mechanism (100) includes an extendable / retractable plunger, wherein the extendable / retractable plunger extends and retracts by an electric motor (102) and a linear drive Wherein the braking device is electrically operated to shrink. The apparatus according to any one of the preceding claims,
The left bracket 3 and the right bracket 6 are respectively supported on the left side and right side portions of the stand 37 and the braking device further includes a shaft turning mechanism 200, Is operable to rotate the rotary shaft by engagement with a flange (39) or a brake disk disposed on the stand and fixed to the rotary shaft.  12. The apparatus according to claim 11, wherein the shaft rotation mechanism (200) comprises a gear wheel (201), the gear wheel comprising a toothed periphery (41) of a flange (39) And is configured to be rotatable with an engageable toothed circumference. 13. A braking device according to claim 12, wherein the gear wheel (201) is electrically rotatable by an electric motor (204) and a bevel gear drive (205). The brake device of claim 1, wherein the brake disk or flange comprises a toothed circumferential portion (41) in an assembly with a rotary shaft having a flange (39) or a brake disk fixed to the rotary shaft. In an assembly having a brake disk or a rotary shaft with a flange (39) fixed to a rotary shaft, the brake disk or flange comprises a plurality of radially inwardly positioned radially inner portions of the brake disk or flange The through holes (42) of the braking device.

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